CN114321107B - Hydraulic control driving system - Google Patents
Hydraulic control driving system Download PDFInfo
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- CN114321107B CN114321107B CN202111335918.8A CN202111335918A CN114321107B CN 114321107 B CN114321107 B CN 114321107B CN 202111335918 A CN202111335918 A CN 202111335918A CN 114321107 B CN114321107 B CN 114321107B
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Abstract
The disclosure provides a hydraulic control driving system, which belongs to the field of mechanical hydraulic control. The hydraulic control driving system comprises a power output unit, a control unit and an execution unit; the control unit comprises a first reversing valve, a first servo valve, a second reversing valve and a third reversing valve; the first servo valve comprises a first main valve, and the second servo valve comprises a second main valve; the first oil port of the second main valve is communicated with the first oil port of the execution unit, the second oil port of the second main valve is communicated with the second oil port of the execution unit, and the two oil outlets of the second main valve are communicated with the oil inlet of the power output unit; and an oil inlet of the second reversing valve is communicated with an oil outlet of the power output unit, and a first oil port of the second reversing valve is communicated with a first control oil port of the first main valve. The hydraulic control driving system can meet the requirements of accuracy and speed control of the execution unit.
Description
Technical Field
The disclosure belongs to the field of mechanical hydraulic control, and in particular relates to a hydraulic control driving system.
Background
A hydraulically controlled drive system is a common power driven device whose function is to convert hydraulic energy into mechanical energy. By inputting the flow and pressure of the fluid in the system, the linear motion (driving the cylinder to move linearly) or the rotational motion (driving the hydraulic motor to rotate) is finally output.
In the related art, a hydraulic control driving system generally adopts a single high-precision servo valve to control an oil cylinder or a hydraulic motor in combination with other valve elements, so that the control precision of the system is high.
However, when the system not only requires high control precision, but also requires that the motion speed is reached in a limited time, the selected servo valve can not meet the speed requirement while meeting the precision due to limited flow and precision of the servo valve, and can not meet the precision while meeting the speed, and finally cannot meet the actual requirement.
Disclosure of Invention
The embodiment of the disclosure provides a hydraulic control driving system which can simultaneously meet the requirements of high-precision position control and high-precision large-section speed control. The technical proposal is as follows:
the embodiment of the disclosure provides a hydraulic control driving system, which comprises a power output unit, a control unit and an execution unit; the control unit comprises a first reversing valve, a first servo valve, a second reversing valve and a third reversing valve; the first servo valve comprises a first main valve, and the second servo valve comprises a second main valve; the oil inlet of the first reversing valve is communicated with the oil outlet of the power output unit, the first oil port of the first reversing valve is communicated with the oil inlet of the first main valve, and the second oil port of the first reversing valve is communicated with the oil inlet of the second main valve; the first oil port of the first main valve is communicated with the first oil port of the execution unit, the second oil port of the first main valve is communicated with the second oil port of the execution unit, and two oil outlets of the first main valve are communicated with the oil inlet of the power output unit; the first oil port of the second main valve is communicated with the first oil port of the execution unit, the second oil port of the second main valve is communicated with the second oil port of the execution unit, and the two oil outlets of the second main valve are communicated with the oil inlet of the power output unit; the oil inlet of the second reversing valve is communicated with the oil outlet of the power output unit, the first oil port of the second reversing valve is communicated with the first control oil port of the first main valve, and the second oil port of the second reversing valve is communicated with the first control oil port of the second main valve; the oil inlet of the third reversing valve is communicated with the oil outlet of the power output unit, the first oil port of the third reversing valve is communicated with the second control oil port of the first main valve, and the second oil port of the third reversing valve is communicated with the second control oil port of the second main valve.
In yet another implementation of the present disclosure, the first servo valve further includes a first shuttle valve; the first oil port of the first shuttle valve is communicated with the third oil port of the first main valve, the second oil port of the first shuttle valve is communicated with the fourth oil port of the first main valve, and the third oil port of the first shuttle valve is communicated with the oil inlet of the first main valve.
In yet another implementation of the present disclosure, the first servo valve further includes a first relief valve; the oil inlet of the first overflow valve is communicated with the first oil port of the first shuttle valve, the oil outlet of the first overflow valve is communicated with the oil inlet of the power output unit, and the control oil port of the first overflow valve is communicated with the oil inlet of the first overflow valve.
In yet another implementation of the present disclosure, the first servo valve further includes a first pressure compensator; the oil inlet of the first pressure compensator is communicated with the first oil port of the first reversing valve, the oil outlet of the first pressure compensator is communicated with the oil inlet of the first main valve, the first control oil port of the first pressure compensator is communicated with the oil outlet of the first pressure compensator, and the first control oil port of the first pressure compensator is communicated with the third oil port of the first shuttle valve.
In yet another implementation of the present disclosure, the first servo valve further includes a third relief valve; the oil inlet of the third overflow valve is communicated with the third oil port of the first shuttle valve, the oil outlet of the third overflow valve is communicated with the oil inlet of the power output unit, and the control oil port of the third overflow valve is communicated with the oil inlet of the third overflow valve.
In yet another implementation of the present disclosure, the control unit further includes a pilot valve; the oil inlet of the control valve is communicated with the oil outlet of the power output unit, the first oil port of the control valve is communicated with the oil inlet of the second reversing valve, and the second oil port of the control valve is communicated with the oil inlet of the third reversing valve.
In yet another implementation of the present disclosure, the control unit further includes a first pressure relief valve; an oil inlet of the first pressure reducing valve is communicated with an oil outlet of the power output unit, and an oil outlet of the first pressure reducing valve is communicated with an oil inlet of the control valve.
In yet another implementation of the present disclosure, the execution unit includes a motor and a balancing valve; the oil inlet of the balance valve is respectively communicated with the first oil port of the first main valve and the first oil port of the second main valve, the working oil port of the balance valve is communicated with the first oil port of the motor, and the control oil port of the balance valve is communicated with the second oil port of the motor; and the second oil port of the motor is respectively communicated with the second oil port of the first main valve and the second oil port of the second main valve.
In yet another implementation of the present disclosure, the execution unit further includes an execution shuttle valve and a brake; the first oil port of the execution shuttle valve is communicated with the oil inlet of the balance valve, the second oil port of the execution shuttle valve is communicated with the second oil port of the motor, and the third oil port of the execution shuttle valve is communicated with the oil inlet of the brake.
In yet another implementation of the present disclosure, the execution unit further includes a second pressure relief valve; and an oil inlet of the second pressure reducing valve is communicated with a third oil port of the execution shuttle valve, and an oil outlet of the second pressure reducing valve is communicated with an oil inlet of the brake.
The technical scheme provided by the embodiment of the disclosure has the beneficial effects that:
when the hydraulic control driving system provided by the embodiment of the disclosure is used, the power output unit is started first, so that hydraulic oil output by the power output unit enters the first reversing valve.
When the hydraulic control driving system is required to drive the execution unit to move at a high speed along the first direction, a large flow of hydraulic oil is required to be input into the second oil port of the execution unit, and the hydraulic oil is required to be output from the first oil port of the execution unit. At the moment, after the valve core of the first reversing valve is controlled to move left, the valve core is positioned at the right position, and the oil inlet of the first reversing valve is communicated with the second oil port. When the hydraulic oil enters the first reversing valve, the hydraulic oil enters the second servo valve from the second oil port of the first reversing valve.
Meanwhile, after the valve core of the second reversing valve is controlled to move left, the valve core is positioned at the right position, and an oil inlet of the second reversing valve is communicated with the second oil port. When the hydraulic oil enters the second reversing valve, the hydraulic oil enters a first control oil port on the left side of a second main valve of the second servo valve from a second oil port of the second reversing valve. The spool of the second main valve is in the leftmost position. The oil inlet of the second main valve is communicated with the second oil port. After the hydraulic oil enters the second main valve, the hydraulic oil enters the second oil port of the execution unit from the second oil port of the second main valve, and the execution unit is driven to move at a high speed along the first direction. Of course, the hydraulic oil output from the second oil port of the execution unit is recovered into the power output unit through the first oil port of the second servo valve.
When the hydraulic control driving system is required to drive the execution unit to move at a low speed along the first direction, low-flow hydraulic oil is required to be input into the second oil port of the execution unit, and hydraulic oil is required to be output from the first oil port of the second oil port. At the moment, after the valve core of the first reversing valve is controlled to move left, the valve core is positioned at the left position, and the oil inlet of the first reversing valve is communicated with the first oil port. When hydraulic oil enters the first reversing valve, the hydraulic oil enters the first servo valve from the first oil port of the first reversing valve.
Meanwhile, after the valve core of the second reversing valve is controlled to move rightwards, the valve core is positioned at the left position, and an oil inlet of the second reversing valve is communicated with the first oil port. When the hydraulic oil enters the second reversing valve, the hydraulic oil enters a first control oil port on the left side of a first main valve of the first servo valve from a first oil port of the second reversing valve. The spool of the first main valve is in the leftmost position. The oil inlet of the first main valve is communicated with the second oil port. After the hydraulic oil enters the first main valve, the hydraulic oil enters the second oil port of the execution unit from the second oil port of the first main valve, and the execution unit is driven to move at a low speed along the first direction. Of course, the hydraulic oil output from the first oil port of the execution unit is recovered into the power output unit through the first oil port of the first main valve.
That is, by controlling the first servo valve and the second servo valve as main control valves for the hydraulic oil input to the actuator unit, respectively, it is possible to make the second servo valve participate in the system operation when the actuator unit is operated at a high speed, and make the first servo valve participate in the system operation when the actuator unit is operated at a low speed.
When the execution unit needs to be driven to move at a high speed along the second direction, the process is similar to that of the first direction, and only the valve cores of the first main valve and the second main valve are respectively positioned at the right position through the third reversing valve. And will not be described in detail here.
According to the embodiment of the disclosure, the first servo valve and the second servo valve are used for respectively controlling the work of the execution unit, so that the execution unit can meet the requirements of precision and speed during acceleration and deceleration.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present disclosure, the drawings required for the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present disclosure, and other drawings may be obtained according to these drawings without inventive effort for a person of ordinary skill in the art.
FIG. 1 is a schematic diagram of a hydraulic control drive system provided by an embodiment of the present disclosure;
FIG. 2 is a schematic diagram of another hydraulic control drive system provided by an embodiment of the present disclosure;
FIG. 3 is a schematic structural view of a first main valve provided by an embodiment of the present disclosure;
fig. 4 is a partial schematic diagram of another hydraulic control drive system provided by an embodiment of the present disclosure.
The symbols in the drawings are as follows:
1. a power output unit; 11. a motor; 12. a main pump; 13. controlling the pump; 14. an oil tank; 15. a cooler; 16. a filter;
2. a control unit; 21. a first reversing valve; 22. a first servo valve; 221. a first main valve; 222. a first shuttle valve; 223. a first overflow valve; 224. a first pressure compensator; 225. a third overflow valve;
23. a second servo valve; 231. a second main valve; 24. a second reversing valve; 25. a third reversing valve; 26. a fourth reversing valve; 27. operating the valve; 28. a first pressure reducing valve;
3. an execution unit; 31. a motor; 32. a balancing valve; 33. executing a shuttle valve; 34. a brake; 35. a second pressure reducing valve; 36. an encoder.
Detailed Description
For the purposes of clarity, technical solutions and advantages of the present disclosure, the following further details the embodiments of the present disclosure with reference to the accompanying drawings.
The embodiment of the present disclosure provides a hydraulic control drive system, as shown in fig. 1, which includes a power output unit 1, a control unit 2, and an execution unit 3. The control unit 2 includes a first directional valve 21, a first servo valve 22, a second servo valve 23, a second directional valve 24, and a third directional valve 25. The first servo valve 22 comprises a first main valve 221 and the second servo valve 23 comprises a second main valve 231. The oil inlet P of the first reversing valve 21 is communicated with the oil outlet of the power output unit 1, the first oil port A of the first reversing valve 21 is communicated with the oil inlet P of the first main valve 221, and the second oil port B of the first reversing valve 21 is communicated with the oil inlet P of the second main valve 231. The first oil port A of the first main valve 221 is communicated with the first oil port A of the execution unit 3, the second oil port B of the first main valve 221 is communicated with the second oil port B of the execution unit 3, and two oil outlets T of the first main valve 221 are both communicated with the oil inlet of the power output unit 1. The first oil port A of the second main valve 231 is communicated with the first oil port A of the execution unit 3, the second oil port B of the second main valve 231 is communicated with the second oil port B of the execution unit 3, and two oil outlets T of the second main valve 231 are communicated with the oil inlet of the power output unit 1. The oil inlet P of the second reversing valve 24 is communicated with the oil outlet of the power output unit 1, the first oil port A of the second reversing valve 24 is communicated with the first control oil port a of the first main valve 221, and the second oil port B of the second reversing valve 24 is communicated with the first control oil port a of the second main valve 231. The oil inlet P of the third reversing valve 25 is communicated with the oil outlet of the power output unit 1, the first oil port A of the third reversing valve 25 is communicated with the second control oil port B of the first main valve 221, and the second oil port B of the third reversing valve 25 is communicated with the second control oil port B of the second main valve 231.
When the hydraulic control drive system provided by the embodiment of the present disclosure is used, the power output unit 1 is started first, so that the hydraulic oil output by the power output unit 1 enters the first directional valve 21.
When the actuator 3 is required to be driven to move at a high speed in the first direction by the hydraulic control driving system, it is necessary to input a large flow of hydraulic oil into the second port B of the actuator 3 and output the hydraulic oil from the first port a of the actuator 3. At this time, after the spool of the first reversing valve 21 is controlled to move left, the spool is positioned at the right position, and the oil inlet P of the first reversing valve 21 is communicated with the second oil port B. When the hydraulic oil enters the first directional valve 21, the hydraulic oil enters the second servo valve 23 from the second oil port B of the first directional valve 21.
Meanwhile, after the valve core of the second reversing valve 24 is controlled to move left, the valve core is positioned at the right position, and the oil inlet P of the second reversing valve 24 is communicated with the second oil port B. When the hydraulic oil enters the second direction valve 24, the hydraulic oil enters the first control port a on the left side of the second main valve 231 of the second servo valve 23 from the second port B of the second direction valve 24. The spool of the second main valve 231 is in the leftmost position. The oil inlet P of the second main valve 231 is communicated with the second oil port B. After the hydraulic oil enters the second main valve 231, the hydraulic oil enters the second port B of the actuator 3 from the second port B of the second main valve 231, and drives the actuator 3 to move at a high speed in the first direction. Of course, the hydraulic oil output from the second port B of the actuator 3 is recovered into the power take-off unit 1 through the first port a of the second servo valve 23.
When the actuator 3 is required to be driven to move at a low speed in the first direction by the hydraulic control driving system, it is required to input a low flow rate of hydraulic oil into the second port B of the actuator 3 and output the hydraulic oil from the first port a of the second port B. At this time, after the spool of the first reversing valve 21 is controlled to move left, the spool is left, and the oil inlet P of the first reversing valve 21 is communicated with the first oil port a. When the hydraulic oil enters the first directional valve 21, the hydraulic oil enters the first servo valve 22 from the first oil port a of the first directional valve 21.
Meanwhile, after the valve core of the second reversing valve 24 is controlled to move rightwards, the valve core is left, and an oil inlet P of the second reversing valve 24 is communicated with the first oil port A. When the hydraulic oil enters the second direction valve 24, the hydraulic oil enters the first control port a on the left side of the first main valve 221 of the first servo valve 22 from the first port a of the second direction valve 24. The spool of the first main valve 221 is in the leftmost position. The oil inlet P of the first main valve 221 is communicated with the second oil port B. After the hydraulic oil enters the first main valve 221, the hydraulic oil enters the second port B of the actuator 3 from the second port B of the first main valve 221, and drives the actuator 3 to move at a low speed in the first direction. Of course, the hydraulic oil output from the first port a of the actuator 3 is recovered into the power take-off unit 1 through the first port a of the first main valve 221.
That is, by controlling the first servo valve 22 and the second servo valve 23 as main control valves for the hydraulic oil input to the actuator 3, respectively, it is possible to make the second servo valve 23 participate in the system operation when the actuator 3 is operated at a high speed, and make the first servo valve 22 participate in the system operation when the actuator 3 is operated at a low speed.
When it is necessary to drive the actuator 3 to move at a high speed in the second direction, the valve bodies of the first main valve 221 and the second main valve 231 are respectively set to the right by the third direction valve 25, similarly to the process when the actuator moves at a high speed in the first direction. And will not be described in detail here.
The embodiment of the disclosure controls the operation of the execution unit 3 through the first servo valve 22 and the second servo valve 23 respectively, so that the execution unit 3 can meet the requirements of precision and speed during acceleration and deceleration.
Illustratively, the first and second servo valves 22, 23 are rated at the same pressure and at different flow rates. The flow rate of the first servo valve 22 is small, the maximum control flow rate is 10% of the flow rate corresponding to the maximum speed of the execution unit 3 during operation, the speed control range of the execution unit 3 is 0.5% -10%, the ratio of the minimum speed to the maximum speed is 20%, and the control precision is high. The second servo valve 23 has a large flow rate, the maximum control flow rate is 90% of the maximum speed corresponding flow rate when the execution unit 3 is operated, and the control accuracy is relatively low.
Fig. 2 is a schematic diagram of another hydraulic control driving system provided in an embodiment of the present disclosure, and in conjunction with fig. 2, alternatively, the power output unit 1 includes an electric motor 11, a main pump 12, a control pump 13, and an oil tank 14, where the electric motor 11 is used to drive the main pump 12 and the control pump 13, an oil inlet of the main pump 12 is communicated with the oil tank 14, and an oil inlet of the control pump 13 is communicated with the oil tank 14.
The electric motor 11 is used for driving the main pump 12 or controlling the pump 13 to rotate, and the oil tank 14 is used for providing power oil for the whole hydraulic control driving system. The main pump 12 is used for pumping power oil for a main oil gallery of the hydraulic control driving system, and the control pump 13 is used for pumping power oil for a control oil gallery of the hydraulic control driving system.
In this embodiment, the main pump 12 is a variable displacement pump, and the main pump 12 is a load-sensitive pump. The variable pump is used as an oil source of the main loop. The control pump 13 is a fixed displacement pump which serves as an oil source for the control circuit. The variable pump and the fixed displacement pump are connected in series and then connected with the motor 11.
In this embodiment, in order to enable the hydraulic oil in the oil tank 14 to meet the actual temperature demand, a thermometer is generally disposed on the side wall of the oil tank 14 so that it is possible to observe in real time whether the temperature in the oil tank 14 meets the actual demand.
In order to ensure that the quantity of oil in the tank 14 meets the requirements of the actual use, it is also usual to arrange a level gauge on the side wall of the tank 14, so that the depth of the hydraulic oil in the tank 14 can be observed in real time by means of the level gauge, in order to determine the volume of hydraulic oil in the tank 14.
Optionally, the power output unit 1 further includes a cooler 15, an oil inlet of the cooler 15 is communicated with an oil outlet T of the first servo valve 22 and an oil outlet T of the second servo valve 23, and an oil outlet of the cooler 15 is communicated with the oil tank 14.
In the above-described implementation, the addition of the cooler 15 may reduce the temperature of the recovered hydraulic oil so that the oil temperature in the oil tank 14 is not too high to affect the use.
Optionally, the power output unit 1 further includes a filter 16, an oil inlet of the filter 16 is communicated with an oil outlet T of the first servo valve 22 and an oil outlet T of the second servo valve 23, and an oil outlet of the filter 16 is communicated with an oil inlet of the cooler 15.
In the above implementation, the addition of the filter 16 can improve the use safety of the hydraulic control driving system, avoid the entry of impurities into the oil tank 14, and further enter the whole oil path again under the driving of the main pump 12, affect the use of each valve element, and also avoid affecting the normal use of the motor 31.
Fig. 3 is a schematic structural view of a first main valve provided in an embodiment of the present disclosure, and fig. 4 is a schematic partial diagram of another hydraulic control driving system provided in an embodiment of the present disclosure, and in conjunction with fig. 3 and fig. 4, the first servo valve 22 may optionally further include a first shuttle valve 222. The first port a of the first shuttle valve 222 communicates with the third port C of the first main valve 221 (see fig. 3), the second port b of the first shuttle valve 222 communicates with the fourth port D of the first main valve 221, and the third port C of the first shuttle valve 222 communicates with the oil inlet P of the first main valve 221.
In the above implementation manner, the first port a and the second port B of the first shuttle valve 222 are respectively communicated with the third port C and the fourth port D of the first main valve 221, and the third port C of the first main valve 221 is communicated with the first port a and the second port B and the fourth port D, so that the first port a and the second port B of the first shuttle valve 222 are respectively communicated with the first port a and the second port B of the first main valve 221, i.e., the pressure of the third port of the first shuttle valve 222 is equal to the larger pressure value in the first port a or the second port B of the first main valve 221, so that the first main valve 221 can be matched with the first pressure compensator 224 to ensure that the pressure at the inlet and the pressure at the outlet of the first main valve 221 are kept constant, so that the first main valve 221 is not affected by flow and load fluctuation, thereby realizing accurate flow control of the first main valve 221.
Optionally, the first servo valve 22 further comprises a first pressure compensator 224. The oil inlet a of the first pressure compensator 224 is communicated with the first oil port a of the first reversing valve 21, the oil outlet b of the first pressure compensator 224 is communicated with the oil inlet P of the first main valve 221, the first control oil port c of the first pressure compensator 224 is communicated with the oil outlet b of the first pressure compensator 224, and the second control oil port d of the first pressure compensator 224 is communicated with the third oil port c of the first shuttle valve 222.
In the above-described implementation, since the pressure of the oil outlet b in the first pressure compensator 224 is equal to the pressure value of the spring in the first pressure compensator 224 and the pressure value of the first control oil port c. Therefore, when the first pressure compensator 224 and the first shuttle valve 222 are provided, the pressure of the oil outlet b in the first pressure compensator 224 is equal to the pressure of the oil inlet P of the first main valve 221. And the working port c of the first shuttle valve 222 communicates with the first control port c of the first pressure compensator 224, so that the pressure of the first control port c of the first pressure compensator 224 is equal to a value where the pressure of the first working port a or the second working port B of the first main valve 221 is greater. That is, the pressure of the first control port c in the first pressure compensator 224 is equal to the pressure at the outlet of the first main valve 221, so that the difference between the pressure at the inlet and the pressure at the outlet of the first main valve 221 is the pressure of the spring in the first pressure compensator 224, that is, the pressure at the inlet and the pressure at the outlet of the first main valve 221 are kept constant, so that the first main valve 221 is not affected by the flow and the load fluctuation, thereby achieving accurate control of the flow of the first main valve 221.
Optionally, the first servo valve 22 further includes a first relief valve 223, an oil inlet a of the first relief valve 223 is communicated with the first oil port a of the first shuttle valve 222, an oil outlet b of the first relief valve 223 is communicated with the oil inlet of the power output unit 1, and a control oil port c of the first relief valve 223 is communicated with the oil inlet a of the first relief valve 223.
In the above-described implementation, the first relief valve 223 plays a role of safety protection, and protects the first main valve 221 by limiting the pressure of the return oil from the first main valve 221.
Optionally, the first servo valve 22 further comprises a third relief valve 225. An oil inlet a of the third overflow valve 225 is communicated with an oil outlet T of the first shuttle valve 222, an oil outlet b of the third overflow valve 225 is communicated with an oil inlet of the power output unit 1, and a control oil port c of the third overflow valve 225 is communicated with an oil inlet a of the third overflow valve 225.
In the above-described embodiment, the third relief valve 225 functions as the first relief valve 223 and also serves as a safety protection function, and the first main valve 221 is protected by limiting the pressure of the return oil from the first main valve 221.
In the present embodiment, the first servo valve 22 and the second servo valve 23 are identical in structure, and the second servo valve 23 will not be described in detail here.
Referring again to fig. 2, optionally, the control unit 2 further includes a fourth reversing valve 26, where an oil inlet P of the fourth reversing valve 26 is communicated with an oil outlet of the power output unit 1, a first oil port a of the fourth reversing valve 26 is communicated with a second control oil port d of the first pressure compensator 224 in the first servo valve 22, and a second oil port B of the fourth reversing valve 26 is communicated with a second control oil port d of the first pressure compensator in the second servo valve 23.
The fourth reversing valve 26 is used for communicating with the second control port d of the first pressure compensator 224 in the first servo valve 22 or the second control port d of the first pressure compensator in the second servo valve 23 to feed back the control oil pressure in the first servo valve 22 or the second servo valve 23 to the power output unit 1, thereby adjusting the output pressure and flow rate of the power output unit 1.
In this embodiment, the fourth reversing valve 26 is communicated with the second control oil port d of the first pressure compensator 224 in the first servo valve 22 through a one-way valve, the oil inlet of the one-way valve is communicated with the second control oil port d of the first pressure compensator 224, and the oil outlet of the one-way valve is communicated with the first oil port a of the fourth reversing valve 26. Similarly, the fourth reversing valve 26 is also communicated with the second control oil port d of the first pressure compensator in the second servo valve 23 through a one-way valve.
Optionally, the control unit 2 further includes a control valve 27, an oil inlet of the control valve 27 is communicated with an oil outlet of the power output unit 1, a first oil port a of the control valve 27 is communicated with an oil inlet P of the second reversing valve 24, and a second oil port a of the control valve 27 is communicated with an oil inlet P of the third reversing valve 25.
In the above embodiment, the pilot valve 27 is used to control the second direction valve 24 and the third direction valve 25. When the pilot valve 27 is operated in the left position, that is, the oil inlet of the pilot valve 27 is communicated with the first oil port a of the pilot valve 27, the pilot valve 27 can connect the second reversing valve 24 with the control pump 13. When the pilot valve 27 works in the right position, that is, the oil inlet of the pilot valve 27 is communicated with the second oil port B of the pilot valve 27, the pilot valve 27 can connect the third reversing valve 25 with the control pump 13.
That is, in order to facilitate control, the second switching valve 24 and the third switching valve 25 are normally powered on or off at the same time, and at this time, the second switching valve 24 or the third switching valve 25 can be controlled by directly controlling the left or right operation of the control valve 27. Further, under the control of the pilot valve 27, the motor 31 can be steplessly regulated. That is, the control hydraulic oil output from the power output unit 1 enters one of the second direction valve 24 and the third direction valve 25 under the control of the pilot valve 27. In this embodiment, the pilot valve 27 is a commercially available off-the-shelf component.
Optionally, the control unit 2 further comprises a first pressure reducing valve 28, an oil inlet of the first pressure reducing valve 28 is communicated with an oil outlet of the power output unit 1, and an oil outlet of the first pressure reducing valve 28 is communicated with an oil inlet of the operating valve 27.
In the above-described implementation, the first relief valve 28 is used to reduce the pressure of the hydraulic oil output in the control pump 13 so that the pressure of the hydraulic oil can satisfy the operating pressure of the pilot valve 27.
Optionally, the execution unit 3 comprises a motor 31 and a balancing valve 32. The oil inlet P of the balance valve 32 is respectively communicated with the first oil port a of the first main valve 221 and the first oil port a of the second main valve 231, the working oil port a of the balance valve 32 is communicated with the first oil port a of the motor 31, and the control oil port X of the balance valve 32 is communicated with the second oil port B of the motor 31. The second port B of the motor communicates with the second port B of the first main valve 221 and the second port B of the second main valve 231, respectively.
In the above implementation manner, the balance valve 32 is used to play a role in supporting the load under the descending condition, so as to avoid the phenomenon of galloping of the motor 31.
Optionally, the execution unit 3 further comprises an execution shuttle valve 33 and a brake 34. The first oil port a of the execution shuttle valve 33 is communicated with the oil inlet P of the balance valve 32, the second oil port B of the execution shuttle valve 33 is communicated with the second oil port B of the motor 31, and the third oil port C of the execution shuttle valve 33 is communicated with the oil inlet of the brake 34 to drive the brake 34 to be opened.
In the above-described implementation, the input pressure of the execution shuttle valve 33 is the higher pressure value of the first port a or the second port B of the motor 31, and the output pressure of the execution shuttle valve 33 acts on the brake 34.
Since the oil inlet of the shuttle valve 33 is the first oil port a or the second oil port B in the motor 31, when the pressure of one of the oil ports is higher than the value, the brake 34 can be kept open when the motor 31 rotates, thereby avoiding braking the motor 31. When the system is unexpected, for example, the motor 31 cannot rotate normally, no oil enters the shuttle valve 33, and the brake 34 is in a closed state, so that the motor 31 can be braked to prevent accidents.
That is, by performing the cooperation of the shuttle valve 33 and the stopper 34, the motor 31 can be ensured to operate normally, avoiding accidents.
In this embodiment, the motor 31 is mounted with the spool to rotate the spool, and the brake 34 is a belt brake, and the brake 34 is sleeved outside the spool. When the brake is tightened and closed, the spool can be braked.
Optionally, the execution unit 3 further includes a second pressure reducing valve 35, an oil inlet of the second pressure reducing valve 35 is communicated with the third oil port C of the execution shuttle valve 33, and an oil outlet of the second pressure reducing valve 35 is communicated with an oil inlet of the brake 34.
In the above-described implementation, the second pressure reducing valve 35 is used to reduce the pressure of the oil outlet of the execution shuttle valve 33.
Optionally, the execution unit 3 further comprises an encoder 36, the encoder 36 being connected to the motor 31.
In the above-described implementation, the encoder 36 is used to detect the rotational speed of the motor 31.
In this embodiment, the hydraulic control driving system further includes a controller, and the controller 100 is electrically connected to the above valve members, respectively, so as to automatically control the above valve members.
The working procedure of the hydraulic control driving system provided by the embodiment of the present disclosure is briefly described below:
first, the motor 11 is started so that the load-sensitive pump passes the hydraulic oil in the oil tank 14 through the oil port of the load-sensitive pump to the oil inlet P of the first reversing valve 21. The hydraulic oil in the oil tank 14 is delivered to the first relief valve 28 through the oil port of the metering pump, and is delivered to the oil inlet of the control valve 27 after being relieved.
Next, according to different operation instructions of the control valve 27, such as lifting or lowering signals, the spool of the control valve 27 is in the left or right position. After the hydraulic oil enters the second reversing valve 24 through the left position of the control valve 27, the left position operation or the right position operation of the second reversing valve 24 is controlled, and the left position operation of the first main valve 221 or the left position operation of the second main valve 231 is driven. Meanwhile, after the hydraulic oil enters the third reversing valve 25 through the right position of the control valve 27, the left position operation or the right position operation of the third reversing valve 25 is controlled, and the right position operation of the first main valve 221 or the right position operation of the second main valve 231 is driven.
Then, the hydraulic oil reaches the first switching valve 21. When the first reversing valve 21 is operated in the left position, hydraulic oil enters the first oil port a or the second oil port B of the first main valve 221 and is delivered to the first oil port a or the second oil port B of the motor 31. When the first reversing valve 21 works in the right position, hydraulic oil enters the first oil port a or the second oil port B of the second main valve 231 and is conveyed to the first oil port a or the second oil port B of the motor 31.
When oil is fed from the first oil port a of the motor 31, the balance valve 32 is in a check valve operating condition. When oil is fed from the second port B of the motor 31, the balance valve 32 operates in a throttle operating mode.
Next, the hydraulic oil is delivered to the second pressure reducing valve 35 through the shuttle valve 33, and then the brake 34 is controlled to be opened, and after the brake 34 is opened, the motor 31 starts to operate. When the rotation speed of the motor 31 reaches the set value of the control system, electromagnets of the second reversing valve 24, the third reversing valve 25, the first reversing valve 21 and the fourth reversing valve 26 are controlled to be powered off, and at the moment, the second servo valve 23 participates in working.
Finally, if a shut down is required, the motor 11 is turned off and the load-sensitive pump is stopped from pumping oil into the hydraulically controlled drive system.
In addition, if the differential requirements are made on the forward and reverse rotation speeds due to the working condition requirements, the control logic implementation of the controller 100 can be directly changed.
The foregoing is merely an alternative embodiment of the present disclosure, and is not intended to limit the present disclosure, any modification, equivalent replacement, improvement, etc. that comes within the spirit and principles of the present disclosure are included in the scope of the present disclosure.
Claims (5)
1. A hydraulic control drive system, characterized in that it comprises a power take-off unit (1), a control unit (2) and an execution unit (3);
the control unit (2) comprises a first reversing valve (21), a first servo valve (22), a second servo valve (23), a second reversing valve (24), a third reversing valve (25), an operating valve (27) and a first pressure reducing valve (28);
-said first servo valve (22) comprises a first main valve (221), said second servo valve (23) comprises a second main valve (231); an oil inlet of the first reversing valve (21) is communicated with an oil outlet of the power output unit (1), a first oil port of the first reversing valve (21) is communicated with an oil inlet of the first main valve (221), and a second oil port of the first reversing valve (21) is communicated with an oil inlet of the second main valve (231); a first oil port of the first main valve (221) is communicated with a first oil port of the execution unit (3), a second oil port of the first main valve (221) is communicated with a second oil port of the execution unit (3), and two oil outlets of the first main valve (221) are communicated with an oil inlet of the power output unit (1); the first oil port of the second main valve (231) is communicated with the first oil port of the execution unit (3), the second oil port of the second main valve (231) is communicated with the second oil port of the execution unit (3), and two oil outlets of the second main valve (231) are communicated with the oil inlet of the power output unit (1); an oil inlet of the second reversing valve (24) is communicated with an oil outlet of the power output unit (1), a first oil port of the second reversing valve (24) is communicated with a first control oil port of the first main valve (221), and a second oil port of the second reversing valve (24) is communicated with a first control oil port of the second main valve (231); an oil inlet of the third reversing valve (25) is communicated with an oil outlet of the power output unit (1), a first oil port of the third reversing valve (25) is communicated with a second control oil port of the first main valve (221), and a second oil port of the third reversing valve (25) is communicated with a second control oil port of the second main valve (231); an oil inlet of the control valve (27) is communicated with an oil outlet of the power output unit (1), a first oil port of the control valve (27) is communicated with an oil inlet of the second reversing valve (24), a second oil port of the control valve (27) is communicated with an oil inlet of the third reversing valve (25), an oil inlet of the first pressure reducing valve (28) is communicated with an oil outlet of the power output unit (1), and an oil outlet of the first pressure reducing valve (28) is communicated with an oil inlet of the control valve (27);
the execution unit (3) comprises a motor (31), a balance valve (32), an execution shuttle valve (33), a brake (34) and a second pressure reducing valve (35); the oil inlet of the balance valve (32) is respectively communicated with the first oil port of the first main valve (221) and the first oil port of the second main valve (231), the working oil port of the balance valve (32) is communicated with the first oil port of the motor (31), the control oil port of the balance valve (32) is communicated with the second oil port of the motor (31), the second oil port of the motor (31) is respectively communicated with the second oil port of the first main valve (221) and the second oil port of the second main valve (231), the first oil port of the execution shuttle valve (33) is communicated with the oil inlet of the balance valve (32), the second oil port of the execution shuttle valve (33) is communicated with the second oil port of the motor (31), the third oil port of the execution shuttle valve (33) is communicated with the oil inlet of the brake (34), the oil inlet of the second pressure reducing valve (35) is communicated with the third oil port of the execution shuttle valve (33), and the oil inlet of the second pressure reducing valve (35) is communicated with the oil outlet of the brake (34).
2. The hydraulic control drive system of claim 1, wherein the first servo valve (22) further comprises a first shuttle valve (222);
the first oil port of the first shuttle valve (222) is communicated with the third oil port of the first main valve (221), the second oil port of the first shuttle valve (222) is communicated with the fourth oil port of the first main valve (221), and the third oil port of the first shuttle valve (222) is communicated with the oil inlet of the first main valve (221).
3. The hydraulic control drive system according to claim 2, wherein the first servo valve (22) further comprises a first relief valve (223);
an oil inlet of the first overflow valve (223) is communicated with a first oil port of the first shuttle valve (222), an oil outlet of the first overflow valve (223) is communicated with an oil inlet of the power output unit (1), and a control oil port of the first overflow valve (223) is communicated with an oil inlet of the first overflow valve (223).
4. The hydraulic control drive system of claim 2, wherein the first servo valve (22) further comprises a first pressure compensator (224);
the oil inlet of the first pressure compensator (224) is communicated with the first oil port of the first reversing valve (21), the oil outlet of the first pressure compensator (224) is communicated with the oil inlet of the first main valve (221), the first control oil port of the first pressure compensator (224) is communicated with the oil outlet of the first pressure compensator (224), and the first control oil port of the first pressure compensator (224) is communicated with the third oil port of the first shuttle valve (222).
5. The hydraulic control drive system according to claim 2, wherein the first servo valve (22) further comprises a third relief valve (225);
an oil inlet of the third overflow valve (225) is communicated with a third oil port of the first shuttle valve (222), an oil outlet of the third overflow valve (225) is communicated with an oil inlet of the power output unit (1), and a control oil port of the third overflow valve (225) is communicated with an oil inlet of the third overflow valve (225).
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| CN114321107A (en) | 2022-04-12 |
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